Laundry Dryer with a Heat Pump System

ABSTRACT

Laundry dryer, with a heat pump system, said heat pump system comprises a refrigerant circuit ( 10 ) for a refrigerant and an drying air stream circuit ( 12 ) for the drying air stream, wherein the refrigerant circuit ( 10 ) includes a compressor ( 14 ) with variable output, a first heat exchanger ( 16 ), variable expansion means ( 18 ) and a second heat exchanger ( 20 ) connected in series and forming a closed loop, the drying air stream circuit ( 12 ) includes the first heat exchanger ( 16 ), the second heat exchanger ( 20 ), a laundry treatment chamber ( 22 ) and at least one air stream fan ( 24 ), the refrigerant circuit ( 10 ) and the air stream circuit ( 12 ) are thermally coupled by the first heat exchanger ( 16 ) and the second heat exchanger ( 20 ), the first heat exchanger ( 16 ) is provided for heating up the air stream and cooling down the refrigerant, and the second heat exchanger ( 20 ) is provided for cooling down the air stream and heating up the refrigerant, wherein a control unit ( 38 ) is provided to adjust the variable expansion means ( 18 ), wherein the control unit ( 38 ) is adapted to adjust the variable expansion means ( 18 ) in response to at least a compressor quantity representative of the operation of the compressor ( 14 ) and/or in response to the drying cycle selected by the user, wherein said quantity is at least one of the following rotational speed of the compressor ( 14 ), supply current/voltage frequency of the compressor motor, absorbed power or current of the compressor ( 14 ).

The present invention relates to a laundry dryer with a heat pump system for a according to the-preamble of claims 1 and 7.

A laundry dryer with a heat pump system is an efficient way to dry laundry by low energy consumption. In a conventional heat pump laundry dryer an air stream flows in a close air stream circuit. The air stream is moved by a fan, passes through a laundry drum, removes water from wet laundry, is then cooled down and dehumidified in an evaporator, heated up in a condenser and at last re-inserted into the laundry drum again. The refrigerant instead is compressed by a compressor, condensed in the condenser, laminated in expansion means and then vaporized in the evaporator.

In the most laundry dryers the heat pump system works in an on-off mode, wherein the compressor has one rotational speed. The operation of the heat pump system can be optimized by a variable rotational speed compressor. However, in this case, the Applicant has found that in order to obtain better performances, variable expansion means can be provided to adapt the lamination work to the variation of the rotational speed of the compressor.

In fact, it has been found that higher rotational speed of the compressor and lower rotational speed of the compressor requires different lamination work for the compressor to operates in an effective way.

EP 1 612 976 A1 discloses a drying apparatus comprising a heat pump system, wherein variable expansion means and the compressing performance of the compressor are controlled in response to the pressure of the refrigerant detected at the outlet of the compressor. However, this control method is complex and requires pressure and temperature sensors and an appropriate feedback line.

It is an object of the present invention to provide a laundry dryer with a heat pump system, in which the lamination work of the expansion means can be adapted by low complexity.

The object of the present invention is achieved by the laundry dryer with a heat pump system according to claim 1

According to the present invention, the laundry dryer comprises a control unit the control unit is adapted to adjust the variable expansion means in response to at least a compressor quantity representative of the operation of the compressor and/or to the drying cycle selected by the user, wherein said compressor quantity is at least one of the following:

rotational speed of the compressor (14),

supply current/voltage frequency of the compressor motor,

absorbed power or current of the compressor (14).

Preferably, the control unit is adapted to monitor or determine the rotational speed of the compressor and/or the supply current/voltage frequency of the compressor motor and/or the absorbed power or current of the compressor and to operate the variable expansion means accordingly.

Preferably, the control unit is adapted to receive signals representative of the rotational speed of the compressor and/or the supply current/voltage frequency of the compressor motor and/or the absorbed power or current of the compressor or the control unit is adapted to receive signal representative of predetermined parameters, which are the basis for the determination of rotational speed of the compressor and/or the supply current/voltage frequency of the compressor motor and/or the absorbed power or current of the compressor.

Preferably, the control unit is adapted to set the variable expansion means to a reduced lamination work, when the output of the compressor is high or starts to increase or increases, the control unit is adapted to set the variable expansion means to an increased lamination work, when the output of the compressor is low or starts to decrease or decreases, output of the compressor being the rotational speed of the compressor and/or the supply current/voltage frequency of the compressor motor and/or the absorbed power or current of the compressor.

Preferably, the laundry dryer comprises at least one drying cycle, in which the compressor operates at different outputs, and/or comprising different drying cycles, wherein the output of the compressor is constant or substantially constant in each drying cycle, but different from drying cycle to drying cycle, wherein the control unit adjusts the variable expansion means according to the drying cycle selected by the user.

Preferably, the control unit is adapted to set the variable expansion means to a reduced lamination work according to an increasing output profile of the compressor for the selected drying cycle and to set the variable expansion means to an increased lamination work according to a decreasing output profile of the compressor for the selected drying cycle.

Preferably, the control unit actuates the compressor to increase the output established by the selected drying cycle, and automatically actuates the variable expansion means to a reduced lamination work, further wherein the control unit actuates the compressor to decrease the output established by the selected drying cycle, and automatically actuates the variable expansion means to an increased lamination work.

Preferably, the variable expansion means comprise at least two capillary tubes wherein at least one of said capillary tubes is switched or switchable by at least one valve.

Preferably, the expansion means comprises at least two parallel series of a capillary tube and a corresponding on-off valve in each case, wherein the capillary tubes have different lengths and/or different cross-sections.

Preferably, the expansion means comprises at least two serial capillary tubes, wherein at least one of the capillary tubes is bypassed by an on-off valve.

Preferably, the capillary tubes have different lengths and/or different cross-sections.

Preferably, the capillary tubes have the same lengths and cross-sections.

Preferably, the expansion means comprises two capillary tubes and a three-way valve, wherein the capillary tubes are alternatingly switchable by the three-way valve and the capillary tubes have different lengths and/or different cross-sections.

Preferably, the expansion means comprises at least one lamination valve including a variable opening degree, so the lamination work at said expansion means is adjustable.

Preferably, the control unit is provided for adapting the lamination work at the expansion means to a warm-up phase and a steady state phase of the process of the heat pump system, wherein the warm-up phase corresponds with a higher lamination work and the steady state phase corresponds with lower lamination work.

The novel and inventive features believed to be the characteristic of the present invention are set forth in the appended claims.

The invention will be described in further detail with reference to the drawings, in which

FIG. 1 shows a schematic diagram of a heat pump system for a laundry dryer according to the present invention,

FIG. 2 shows a detailed schematic diagram of expansion means of the heat pump system for the laundry dryer according to a first embodiment of the present invention,

FIG. 3 shows a detailed schematic diagram of expansion means of the heat pump system for the laundry dryer according to a second embodiment of the present invention,

FIG. 4 shows a detailed schematic diagram of expansion means of the heat pump system for the laundry dryer according to a fourth embodiment of the present invention,

FIG. 5 shows a detailed schematic diagram of expansion means of the heat pump system for the laundry dryer according to a fifth embodiment of the present invention,

FIG. 6 shows a schematic diagram of the power and motor frequency as function of time for a compressor of the heat pump system for the laundry dryer according to the present invention,

FIG. 7 shows a schematic diagram of the motor frequencies as function of time for the compressor of the heat pump system for the laundry dryer according to the present invention,

FIG. 8 shows a schematic diagram of the motor speeds as function of time for the compressor of the heat pump system for the laundry dryer according to the present invention,

FIG. 9 shows a schematic diagram of the motor frequency as function of time for the compressor of the heat pump system for the laundry dryer according to the present invention, and

FIG. 10 shows a schematic diagram of the motor speeds as function of time for the compressor of the heat pump system for the laundry dryer according to the present invention.

FIG. 11 shows a schematic diagram of a refrigerant circuit of the heat pump system with a control unit for the laundry dryer according to the present invention.

FIG. 1 illustrates a schematic diagram of a heat pump system for a laundry dryer according to a first embodiment of the present invention. The heat pump system includes a closed refrigerant circuit 10 and a drying air stream circuit 12.

The drying air stream circuit 12 is preferably a closed loop in which the process air is continuously circulated through the laundry storing chamber. However it may also be provided that a (preferably smaller) portion of the process air is exhausted from the process air loop and fresh air (e.g. ambient air) is taken into the process air loop to replace the exhausted process air. And/or the process air loop is temporally opened (preferably only a short section of the total processing time) to have an open loop discharge.

The refrigerant circuit 10 includes a compressor with variable output 14, a first heat exchanger 16, variable expansion means 18 and a second heat exchanger 20. The compressor 14, the first heat exchanger 16, the variable expansion means 18 and the second heat exchanger 20 are switched in series and form a closed loop.

The drying air stream circuit 12 includes the first heat exchanger 16, the second heat exchanger 20, a laundry treatment chamber 22, preferably a rotatable drum 22 and a drying air stream fan 24. The first heat exchanger 16 and the second heat exchanger 20 form the thermal coupling between the refrigerant circuit 10 and the drying air stream circuit 12.

The refrigerant circuit 10 is subdivided into a high pressure portion and a low pressure portion. The high pressure portion extends from the outlet of the compressor 14 via the first heat exchanger 16 to the inlet of the variable expansion means 18. The low pressure portion extends from the outlet of the variable expansion means 18 via the second heat exchanger 20 to the inlet of the compressor 14.

In this example, the first heat exchanger 16 acts as a condenser, and the second heat exchanger 20 acts as an evaporator. However, when the refrigerant operates at least at the critical pressure in the high pressure portion of the refrigerant circuit 10, then the first heat exchanger 16 acts as a gas cooler since the refrigerant is in the gaseous state during the cycle. Similar, when the refrigerant operates at least at the critical pressure in the low pressure portion of the refrigerant circuit 10, then the second heat exchanger 16 acts as a gas heater since the refrigerant is in the gaseous state during the cycle.

The compressor 14 with variable output compresses and heats up the refrigerant. The first heat exchanger 16 cools down the refrigerant in the refrigerant circuit 10 and heats up the air stream in the drying air stream circuit 12, before the air stream is re-inserted into the laundry drum 26. The variable expansion means 18 laminates the refrigerant from a higher pressure to a lower pressure. The second heat exchanger 20 cools down and dehumidifies the air stream, after said air stream has passed the laundry drum 22 in the drying air stream circuit 12. The drying air stream is driven by the air stream fan 24. The output of the compressor 14 is adjustable.

The compressor 14 with variable output is adapted to treat different refrigerant mass flow rate depending on the rotation speed thereof. An electronic controller is provided to change the rotational speed of the electric motor of the compressor in response to a predetermined feedback.

As an example, the electronic controller can vary the operating frequency of the current/voltage absorbed by the compressor electric motor in order to adjust the rotational speed and the power of the compressor. The electronic controller can be an inverter, which drives the electric motor of the compressor 14.

The laundry dryer comprises a control unit 38 connected to the compressor 14 via a compressor control line 44. The control unit 38 is adapted to control the compressor 14 so as to vary the rotational speed and/or the supply current/voltage frequency and/or power/current absorbed by the compressor.

The control unit 38 operates the electronic controller (e.g. inverter) so as to drive the electric motor of the compressor 14.

Rotational speed of the compressor is the speed of the shaft connected to the device that compresses the refrigerant during the compressor running, the rotational speed is substantially equals to the rotational speed of the motor. Supply current/voltage frequency is the frequency of the current/voltage supplied to the compressor motor by the electronic controller to vary the rotational speed of the compressor.

Additionally, the laundry dryer can comprise a drying cycle (operation mode) in which the rotational speed and/or the supply current/voltage frequency and/or power/current absorbed by the compressor varies over the drying time. In addition or alternatively, the laundry dryer can comprise at least two operational modes in which the compressor output is substantially constant or at least substantially constant over most of the drying time but the output is different from one cycle to another.

Preferably, the laundry dryer comprises a control panel 40 for the user to select the available operation modes of the drying cycle/s. The control unit 38 is adapted to receive from the control panel 40 information regarding the drying cycle selected by the user.

It has to be noted that the control unit 38 may be a stand-alone electronic unit, or it may be included in a system which performs overall control of the laundry dryer, including interfacing with a user to display operational information, select drying programs (i.e. control panel) and set operational parameters for such programs.

Additionally the electronic controller (e.g. inverter) can be integrated in the control unit 38.

The user can select different operation modes of the drying cycle/s on said control panel 40 via, for example, a suitable changeover switch 46. For example, a fast operation mode corresponds with a relative high rotational speed of the compressor 14. Further, an eco (or night) mode corresponds with a lower rotational speed of the compressor 14. In dependence of the selection of the user, the control unit activates the corresponding rotational speed of the compressor 14.

Clearly other operation modes can be envisaged having specific output of the compressor for drying different type of textile, different weight of the laundry, for achieving different drying degree of the laundry.

FIG. 6 shows an exemplary schematic diagram of the power P and supply current/voltage frequency f as function of time t for the compressor 14. FIG. 7 clarifies further the relation between the power P and the supply current/voltage frequency f.

FIG. 6 shows a first supply current/voltage frequency f1 and a corresponding first power P1 as well as a second supply current/voltage frequency f2 and a corresponding second power P2. The frequencies f1 and f2 decrease during the drying cycle, while the corresponding powers P1 and P2 remain constant.

The rotational speed of the compressor is linked to the supply current/voltage frequency f.

FIG. 7 shows a schematic diagram of the supply current/voltage frequencies f3 and f4 as function of time t for the compressor 14. The supply current/voltage frequency f3 is higher than the supply current/voltage frequency f4. The supply current/voltage frequency f3 relates, for example, to the fast mode of the drying cycle as previously mentioned. The supply current/voltage frequency f4 relates, for example, to the eco (or night) mode of the drying cycle. The drying cycle of the eco mode requires more time than the drying cycle of the fast mode but less energy.

FIG. 8 shows a schematic diagram of the motor speeds v3 and v4 as function of time t for the compressor 14 of the heat pump system for the laundry dryer according to the present invention. The motor speed v3 is higher than the motor speed v4. The motor speed v3 can relate, for example, to the fast mode of the drying cycle. The motor speed v4 can relate, for example, to the eco (or night) mode of the drying cycle. The drying cycle of the eco mode requires more time than the drying cycle of the fast mode but less energy.

FIG. 9 shows a schematic diagram of the supply current/voltage frequency f as function of time for the compressor 14 that represent another possible operation mode. In FIG. 10 the supply current/voltage frequency f has been reduced after about the half time of the drying cycle.

FIG. 10 shows a schematic diagram of the motor speeds v3 and v4 as function of time for the compressor 14. The motor speed v3 relates, for example, to another possible fast mode of the drying cycle. The motor speed v4 relates, for example, to another possible eco mode of the drying cycle. In both cases the motor speeds v3 and v4 are reduced during the drying cycle. In the fast mode, the motor speed v3 is reduced after the half time of the drying cycle. In the eco mode, the motor speed v4 is reduced after about one third of the time of the drying cycle. The drying cycle of the eco mode requires more time than the drying cycle of the fast mode but less energy.

The variable expansion means 18 provide different lamination work according to the operational conditions of the heat pump system. The control unit 38 is connected to the variable expansion means 18 via a control line 42. The variable expansion means 18 are controlled in response to signal issued by the control unit 38 so as to adjust the pressure drop.

The variable expansion means can include at least two capillary tubes switchable by the control unit 38 to provide different lamination work. FIGS. 2 to 6 show some exemplary arrangements of above mentioned type that will be described in details in the following.

Alternatively the variable expansion means can include a variable expansion valve controllable by the control unit 38, for example the valve can be an electronic valve.

FIG. 2 shows a detailed schematic diagram of expansion means 18 of the heat pump system for the laundry dryer according to an embodiment of the present invention. The expansion means 18 of the first embodiment include a three-way valve 26, a first capillary tube 28 and a second capillary tube 30.

The three-way valve 26 comprises three ports. A first port is connected to the outlet of the first heat exchanger 16. A second port is connected to the inlet of the first capillary tube 28. A third port is connected to the inlet of the second capillary tube 30.

The three-way valve 26 is provided to change over between the first capillary tube 28 and the second capillary tube 30, so that the refrigerant flows either through the first capillary tube 28 or through the second capillary tube 30. The first capillary tube 28 and the second capillary tube 30 have different geometric properties, so that the first capillary tube 28 and the second capillary tube 30 provide different lamination works.

In the example proposed, the lamination work increases with the length of the capillary tubes 28 and 30, assuming that the cross-section of the tubes is the same and the refrigerant flow rate is the same as well. The first capillary tube 28 is shorter than the second capillary tube 30. Thus, the second capillary tube 30 provides higher lamination work than the first capillary tube 28.

However, in a similar manner the lamination work increases with the increasing of the cross-section of the capillary tubes 28 and 30, assuming that the length of the tubes is the same and the refrigerant flow rate is the same as well.

In an alternative embodiments The three-way valve 26 can be arranged downstream of first capillary tube 28 and the second capillary tube 30.

FIG. 3 shows a detailed schematic diagram of expansion means 18 of the heat pump system for the laundry dryer according to another embodiment of the present invention. The expansion means 18 of the embodiment shown include the first capillary tube 28, the second capillary tube 30, a first on-off valve 32 and a second on-off valve 34.

The inlets of the first capillary tube 28 and the second capillary tube 30 are connected to the outlet of the first heat exchanger 16. The outlet of the first capillary tube 28 is connected to the inlet of the first on-off valve 32. In a similar way, the outlet of the second capillary tube 30 is connected to the inlet of the second on-off valve 34. Thus, the on-off valves 32 and 34 are arranged downstream the corresponding capillary tubes 28 and 30, respectively. The outlets of the first on-off valve 32 and the second on-off valve 34 are connected to the inlet of the second heat exchanger 20.

The first on-off valve 32 and the second on-off valve 34 are provided to select one of the capillary tubes 28 or 30. The first capillary tube 28 and the second capillary tube 30 have different geometric properties, so that the first capillary tube 28 and the second capillary tube 30 provides different lamination work. Since the first capillary tube 28 is shorter than the second capillary tube 30, the second capillary tube 30 provides higher lamination work than the first capillary tube 28 (assuming that the respective cross sections are the same).

Additionally, when both the on-off valve 32, 34 are in open position, the first and second capillary tube 28, 30 provide a cumulative lamination work different from the one generated by the first capillary tune 28 when only the first on-off valve 32 is open and by the second capillary tube 30 when only the second on-off valve 32 is open.

FIG. 4 shows a detailed schematic diagram of expansion means 18 of the heat pump system for the laundry dryer according to another embodiment of the present invention. The expansion means 18 of the embodiment shown include the first capillary tube 28, the second capillary tube 30 and the by-pass on-off valve 36.

The inlet of the first capillary tube 28 is connected to the outlet of the first heat exchanger 16. The inlet of the second capillary tube 30 is connected to the outlet of the first capillary tube 28. The outlet of the second capillary tube 30 is connected to the inlet of the second heat exchanger 20. Thus, the first capillary tube 28 and the second capillary tube 30 are connected in series. The bypass on-off valve 36 is connected in parallel to the first capillary tube 28.

Preferably, the bypass on-off valve 36 is provided along a bypass line comprising a bypass line inlet arranged between the inlet of the first capillary tube 28 and the outlet of the first heat exchanger 16 and a bypass line outlet arranged between the outlet of the first capillary tube 28 and inlet of the second capillary tube 30.

When the bypass on-off valve 36 is closed, then the refrigerant flows in the first capillary tube 28 and the second capillary tube 30. When the bypass on-off valve 36 is open, then the first capillary tube 28 is bypassed, and the refrigerant flows only in the second capillary tube 30. When the bypass on-off valve 36 is open, then the lamination work of the expansion means 18 decreases.

FIG. 5 shows a detailed schematic diagram of expansion means 18 of the heat pump system for the laundry dryer according to another embodiment of the present invention. The expansion means 18 of the embodiment shown include the first capillary tube 28, the second capillary tube 30 and the by-pass on-off valve 36.

The inlet of the first capillary tube 28 is connected to the outlet of the first heat exchanger 16. The inlet of the second capillary tube 30 is connected to the outlet of the first capillary tube 28. The outlet of the second capillary tube 28 is connected to the inlet of the second heat exchanger 20. Thus, the first capillary tube 28 and the second capillary tube 30 are connected in series. The bypass on-off valve 36 is connected in parallel to the second capillary tube 30.

Preferably, the bypass on-off valve 36 is provided along a bypass line 38 comprising a bypass line inlet arranged between the outlet of the first capillary tube 28 and the inlet of second capillary tube 30 and a bypass line outlet arranged between the outlet of the second capillary tube 30 and inlet of the second heat exchanger 20.

When the bypass on-off valve 36 is closed, then the refrigerant flows in the first capillary tube 28 and the second capillary tube 30. When the bypass on-off valve 36 is open, then the second capillary tube 30 is bypassed, and the refrigerant flows only in the first capillary tube 28. When the bypass on-off valve 36 is open, then the lamination work of the expansion means 18 decreases.

In the above embodiments the expansion means 18 include two capillary tubes 28 and 30 in each case, wherein two different lamination work can be selected. In general, the expansion means 18 may include more capillary tubes 28 and 30 and/or more valves 26, 32, 34 and/or 36, so that more than two different lamination work can be selected.

The control unit 38 controls the valves 26, 32, 34 and/or 36 of the variable expansion means 18, so that the lamination work at said variable expansion means 18 is adapted to operational condition of the heat pump system.

According to the present invention, the control unit 38 adjusts the variable expansion means 18 in response to the rotational speed of the compressor, the supply current/voltage frequency f of the compressor motor and/or the absorbed power or current of the compressor 14.

In practise, the control unit 38 is adapted to monitor or determine the rotational speed of the compressor and/or the supply current/voltage frequency f of the compressor motor and/or the absorbed power or current of the compressor 14 and to operate the variable expansion means accordingly.

Preferably via the compressor control line 44 provided between the control unit 38 and the compressor 14, the control unit 38 is adapted to receive signals representative of the rotational speed of the compressor and/or the supply current/voltage frequency f of the compressor motor and/or the absorbed power or current of the compressor 14 or is adapted to receive signal representative of predetermined parameters, which are the basis for the determination of rotational speed of the compressor and/or the supply current/voltage frequency f of the compressor motor and/or the absorbed power or current of the compressor 14.

The control unit 38 sets the variable expansion means 18 to a reduced lamination work, when the output of the compressor 14 is high or is getting higher or start to increase, i.e. high speed, high supply current/voltage frequency and high absorbed power or current.

Conversely, the control unit 38 sets the variable expansion means 18 to an increased lamination work, when the output of the compressor 14 is low or is getting lower o start to decrease.

The adjusting of the variable expansion means 18 is performed by a change of the opening degree of the controllable valve or by selecting the most suitable capillary tube from a plurality of capillary tubes 28 and 30 so that the lamination work generated by the variable expansion means 18 is fitted, in an effective way, to the compressor variable output. The opening degree of the controllable valve can be adjusted continuously.

According to another aspect of the present invention, when the laundry dryer includes at least one drying cycle, in which the compressor operates at different outputs, then the control unit 38 adjusts the variable expansion means 18 according to the drying cycle selected by the user. When the laundry dryer includes different drying cycles, wherein the output is constant (or substantially constant) in each drying cycle, but different from drying cycle to drying cycle, then controller adjusts also the variable expansion means 18 according to the drying cycle selected by the user.

The control unit 38 is adapted to set the variable expansion means 18 to a reduced lamination work according to an increasing output profile of the compressor 14 for the selected drying cycle and to set the variable expansion means 18 to an increased lamination work according to a decreasing output profile of the compressor 14 for the selected drying cycle.

Increasing/decreasing output profile means and increasing/decreasing of the compressor rotational speed and/or the supply current/voltage frequency f of the compressor motor and/or the absorbed power or current of the compressor.

In practise, when the control unit 38 has to actuate the compressor 14 to increase the output established by the selected drying cycle, then the control unit 38 automatically actuates the variable expansion means 18 to a reduced lamination work and when the control unit 38 has to actuate the compressor to decrease the output established by the selected drying cycle, then the control unit 38 automatically actuates the variable expansion means 18 to an increased lamination work.

A further application of the variable expansion means 18 may be an adaption of the pressure drop between a warm-up phase and a steady state phase of the laundry dryer. During the warm-up phase of the laundry dryer, a certain lamination work is advantageous in order to shorten said warm-up phase. When the warm-up phase is over, then the lamination work is adjusted to fit the steady state phase.

Although illustrative embodiments of the present invention have been described herein with reference to the accompanying drawings, it is to be understood that the present invention is not limited to those precise embodiments, and that various other changes and modifications may be affected therein by one skilled in the art without departing from the scope or spirit of the invention. All such changes and modifications are intended to be included within the scope of the invention as defined by the appended claims.

LIST OF REFERENCE NUMERALS

10 refrigerant circuit

12 air stream circuit

14 compressor

16 first heat exchanger, condenser

18 expansion means

20 second heat exchanger, evaporator

22 laundry drum

24 air stream fan

26 three-way valve

28 first capillary tube

30 second capillary tube

32 first on-off valve

34 second on-off valve

36 bypass on-off valve

38 control unit

40 control panel

42 control line

44 compressor control line

46 changeover switch

f supply current/voltage frequency

f1 first supply current/voltage frequency

f2 second supply current/voltage frequency

f3 supply current frequency/voltage for the fast mode

f4 supply current frequency/voltage for the eco mode

P power

P1 first power

P2 second power

v motor speed

v3 motor speed for the fast mode

v4 motor speed for the eco mode

t time 

1. A laundry dryer with a heat pump system, said heat pump system comprises a refrigerant circuit (10) for a refrigerant and an drying air stream circuit (12) for the drying air stream, wherein the refrigerant circuit (10) includes a compressor (14) with variable output, a first heat exchanger (16), variable expansion means (18) and a second heat exchanger (20) connected in series and forming a closed loop, the drying air stream circuit (12) includes the first heat exchanger (16), the second heat exchanger (20), a laundry treatment chamber (22) and at least one air stream fan (24), the refrigerant circuit (10) and the air stream circuit (12) are thermally coupled by the first heat exchanger (16) and the second heat exchanger (20), the first heat exchanger (16) is provided for heating up the air stream and cooling down the refrigerant, and the second heat exchanger (20) is provided for cooling down the air stream and heating up the refrigerant, wherein a control unit (38) is provided to adjust the variable expansion means (18), characterized in, that the control unit (38) is adapted to adjust the variable expansion means (18) in response to at least a compressor quantity representative of the operation of the compressor (14) and/or in response to the drying cycle selected by the user, wherein said quantity is at least one of the following: rotational speed of the compressor (14), supply current/voltage frequency of the compressor motor absorbed power or current of the compressor (14).
 2. Laundry dryer according to claim 1, wherein the control unit (38) is adapted to monitor or determine at least one of the compressor quantity and to operate the variable expansion means (18) accordingly.
 3. Laundry dryer according to claim 2, wherein the control unit (38) is adapted to receive signals representative of at least one of the compressor quantity or the control unit (38) is adapted to receive signal representative of predetermined parameters, which are the basis for the determination of at least one of the compressor quantity.
 4. Laundry dryer according to any of the preceding claims, wherein the control unit (38) is adapted to set the variable expansion means (18) to a reduced lamination work, when the at least one of the compressor quantity is high or starts to increase or increases, the control unit (38) is adapted to set the variable expansion means (18) to an increased lamination work, when the at least one of the compressor quantity is low or starts to decrease or decreases.
 5. Laundry dryer according to claim 1, comprising at least one drying cycle, in which the compressor (14) operates at different outputs, and/or comprising different drying cycles, wherein the at least one of the compressor quantity is constant or substantially constant in each drying cycle, but different from drying cycle to drying cycle, wherein the control unit (38) adjusts the variable expansion means (18) according to the drying cycle selected by the user.
 6. Laundry dryer according to claim 5, wherein the control unit (38) is adapted to set the variable expansion means (18) to a reduced lamination work according to an increasing of the at least one of the compressor quantity for the selected drying cycle and to set the variable expansion means (18) to an increased lamination work according to a decreasing of at least one of the compressor quantity for the selected drying cycle.
 7. Laundry dryer according to claim 5 or 6, wherein the control unit (38) actuates the compressor (14) to increase the at least one of the compressor quantity according to the selected drying cycle, and automatically actuates the variable expansion means (18) to a reduced lamination work, further wherein the control unit (38) actuates the compressor to decrease the at least one of the compressor quantity according to selected drying cycle, and automatically actuates the variable expansion means (18) to an increased lamination work.
 8. Laundry dryer according to any of the preceding claims, wherein the variable expansion means (18) comprise at least two capillary tubes (28, 30), wherein at least one of said capillary tubes (28, 30) is switched or switchable by at least one valve (26; 32, 34; 36).
 9. Laundry dryer according to claim 8, wherein the expansion means (18) comprises at least two parallel series of a capillary tube (28, 30) and a corresponding on-off valve (32, 34) in each case, wherein the capillary tubes (28, 30) have different lengths and/or different cross-sections.
 10. Laundry dryer according to claim 8, wherein the expansion means (18) comprises at least two serial capillary tubes (28, 30), wherein at least one of the capillary tubes (28, 30) is bypassed by an on-off valve (36).
 11. Laundry dryer according to any of the preceding claims 8-10, wherein the capillary tubes (28, 30) have different lengths and/or different cross-sections.
 12. Laundry dryer according any of the preceding claims 8-10, wherein the capillary tubes (28, 30) have the same lengths and cross-sections.
 13. Laundry dryer according to any of the preceding claims 8-12, wherein the expansion means (18) comprises two capillary tubes (28, 30) and a three-way valve (26), wherein the capillary tubes (28, 30) are alternatingly switchable by the three-way valve (26) and the capillary tubes (28, 30) have different lengths and/or different cross-sections.
 14. Laundry dryer according any of the preceding claims 1-7, wherein the expansion means (18) comprises at least one lamination valve including a variable opening degree, so the pressure drop at said expansion means (18) is adjustable.
 15. The laundry dryer according to any one of the claims, wherein the control unit (38) is provided for adapting the lamination work at the expansion means (18) to a warm-up phase and a steady state phase of the process of the heat pump system, wherein the warm-up phase corresponds with a higher lamination work and the steady state phase corresponds with lower lamination work. 